Patent GB-1068511-A (GB)
Title: Parallel redundant hydraulic actuator
Inventor: BARLTROP RICHARD KENNETH
IPC: F15B18/00
Filed: 1963-01-01
Abstract: 1,68,511. Fluid pressure servomotor systems. ELLIOTT BROS. (LONDON) Ltd. Dec.31, 1963 [Jan. 1, 1963], No.61/63. Heading G3P. feedback to the amplifiers equalize A parallel redundant hydraulic actuator comprises a plurality of systems each of which includes a fixed primary cylinder such as 12, Fig.1, housing a primary piston 16 and a secondary cylinder 20, which may be formed in the piston 16, housing a secondary piston 24. The primary pistons 16-19 are connected by linkage 35-39 to an output member 40 and the secondary pistons 24-27 are rigidly connected to each other and the output member. A constant hydraulic pressure is supplied to the left hand side of pistons 16-19 and flows into the secondary cylinders 20-23 through orifices 50-53 and by way of restrictions 54-57 in pistons 24-27 to the opposite side of the secondary pistons. The pressure on the right hand side of the primary pistons 16-19 is controlled by electrically operated valves 41 controlled through a common lever 45 acting on transducers 44 to supply an input to amplifiers 43. An electrical feedback to the amplifiers is provided through line 48 responsive to the position of the primary pistons. In operation the primary pistons are actuated by the control of the valves 41 to provide movement of the member 40 and in so doing the secondary pistons also move with the primary pistons. If one of the systems fails e.g. if its valve 41 sticks open, the pressure on the right hand side would increase to move the piston, say 16, to the left. Such movement is opposed by the dashpot effect of the secondary pistons 20-23 until flow of oil through the restrictions 54-57 allows movement of the piston 16 and the output member 39 at a limited rate. This movement continues until the piston 16 is arrested by stops or the piston 'bottoms' on secondary piston 24. The movement of the output member is equal to 1/n of the relative displacement between the primary and secondary pistons, where n is the number of systems. If the failed system is now by-passed, the output moves to the left slowly until one of the secondary pistons 'bottoms' on its primary piston this being achieved by the linkage 35 or 36. In a modification the piston rods of both the primary and secondary pistons extend either side of the pistons to equalize the pressure areas. In a further modification the secondary cylinders are separate from the primary pistons, the secondary piston being rigidly connected to the primary piston and the secondary cylinders to the output member. In Fig. 4 (not shown) the primary pistons (16-19) have passages (96-99) and (100-103) whereby movement of the piston controls the fluid pressure actuation of the secondary pistons (24-27) to follow the movement of the primary pistons until secondary pistons partially cover the passages (100-103) and the forces on the pistons are equalized. In the event of failure as above, the primary piston, say (16), moves until it 'bottoms' on the secondary piston (24) but the remaining systems prevent movement of the output member.